Crankshaft lathe



March 31, 1936- w. F. GROENE El AL CRANKS HAFT LATH E Original Filed July 2, 1930 7 Sheets-Sheet 1 ATTORN EYS March 31, 1936 w GRQENE 5 Re. 19,905

CRANKSHAFT LATHE Original Filed July 2, 1930 7 Sheets-Sheet 2 U/ll zzz am 3. Graeme. George W. Lunmg'.

INVENTORS ATTORNEY March 31, 1936. w GROENE r AL Re. 19,905

CRANKSHAFT LATHE Original Filed July 2, 1930 7 Sheets-Sheet 3 m flm ME NE W w 6 s m w 4 T a km m m m y m W w eorgs J I fia/n l: Q inH ATTORNEYS w. F. GROENE ET AL Re. 19,905

March 31, 1936.

CRANKSHAF'T LATHE Original Filed July 2, 1950 '7 Sheets-Sheet 4 ufi zza am Gr'oene,

G g W g INVENTORS ATTORNEYS March 31, 1936. w GROENE ET AL Re. 19,905

CRANKSHAFT LATHE Original Filed July 2, 1930 7 Sheets-Sheet 5 William j roene, N Gcwge W Jun/h INVENTORE allow-I 31114 ATTORNEYS March 31, 1936. w GRQENE r AL Re. 19,905

CRANKSHAFT LATHE Original Filed July 2, 1930 '7 Sheets-Sheet 6 z'iiz'am f 6]"06726. eorge 14 an 1 120 INVENTOR ATTORNEYS March 31, 1936. w F GRQENE r Re. 19,905

GRANKSHAFT LATHE Original Filed July 2, 1930 '7 Sheets-Sheet 7 ll "min" 1.

jz/ 1 1/4 lfl/lll/lw ///////////A (/1 Mark mmmk mwkto Mm Ll/7722? J? 6/0 ene George mocm'lg INVENTORS ATTORNEY? Reissued Mar. 31, 1936 UNITED STATES PATENT OFFICE CRANKSHAFT LATHE Original No. 1,934,976, dated November 14, 1933,

Serial No. 465,405, July 2, for reissue October 17, 1934,

49 Claims.

This invention pertains to a class of machines known as crank shaft lathes and has for its purpose, the turning of parts of a crank shaft for an internal combustion engine and more particuiarly for turning all line bearing and end parts of a crank shaft at one operation.

Heretofore, it has been considered impossible to turn the flange end, the line bearings and the stub end of a crank shaft in one operation, due to the difflculties encountered in holding the work during the turning operations and in prevent torsional strains which tend to throw out of z, the crank pins and other perm of the l: halt, the work heretofore having been ;,.ie as separate operations on several lathes.

this tendency to torsional strain and deflection h s been overcome in a novel manner in i .e of this application, both in the means ping and holding the shaft and in the tools that work upon the crank shaft, the tools having approach and working positions that counteract the torsional strains set up by each set of of; they remove the metal.

e lathe has a system of loading (as set forth Groene Patent 1,700,721, dated January 1 which prevents any possible damage to ti It also has a sysa hydraulic source er that automatically decreases the rate of feed for the tools as they approach the end of the cut.

The lathe further has a dwell or sizing period, wherein the tools remain without inward or outward travel but in contact with the shaft during a predetermined length of time and then, without effort on the part of the operator, are retraced at rapid traverse to a. position of retreat ready for approach to the next shaft and for permitting the unloading and reloading of the machine.

There is also an arrangement, as will be set forth in the specification wherein power for the various movements and operations is controlled automatically and without effort on the part of the operator.

It may be here stated that the hydraulic features of the machine may have their source of power furnished by any one of several commercial types of hydraulic pumps, the particular one herein illustrated being known as the Oilgear pump.

It is to be further understood that certain of the control features of the crank shaft lathe to be described by this specification are linked to control valves in the Oilgear pump. these valves 1930. Application Serial No. 748,720

being an integral part of the illustrated pump; and their action will be described, but not illustrated, in this application, they being well known in the art.

In our present machine there is flexibility to the working structure where called for and a high degree of resistance to distorting forces which interfere with accuracy or workmanship, which features are a part of the object of the invention, as will be set forth.

In the particular embodiment of our invention selected for illustration:

Figure l is a front elevation, in perspective of our complete machine with all of its accessories,

Fig. 2 is a vertical transverse section on line D of Figs, 3, a and 8, certain of the parts shown in broken section,

Fig. 3 is a rear elevation of the lathe, the pump and motor drives and other accessories being omitted,

Fig, 4 is a front elevation of the left end of the bed of the lathe, with the control levers and the pump accessory,

Fig. 5 is a side elevation of the right hand side of the lei t end ring gear chuck body.

Fig. 6 is a side elevation of the left hand side of the left end ring gear chuck body, the sections being on lines C and 11 of Figs, 1, 3, 4 and 8,

Fig. 7 is a front elevation of one of the ring gear chucks, part of the rim and its housing being in section on line E of Figs. 5 and 6,

Fig. 8 is a side elevation of a rough crank" shaft forging after it has been turned in our lathe, and

Fig. 9 is a diagrammatic layout of the work cycle of the feed for the tools.

Referring now to the drawings, the base of the machine is shown at I and the lathe center housings 2 are bolted thereto. Passing through passage ways 3 in the housings 2, and mounted in bearings 4, bolted to the base, is a drive shaft 5, this shaft being splined as at 6, Figs. 2 and 6, where it passes across the lathe, in the space between the housings 2. The shaft passes through a pair of chuck housings l0. and these housings have mounted in hearings in their lower rear edge, pinions 1 for-drivlng the pair of ring gear chucks, these plnions having splined engagement with the shaft 5. The splim'ng of the shaft and the mounting of the pinions in bearings in the chuck housings makes it possible to shift the chuck housings to any position along the shaft if necessary.

The shaft 5 has on its outer right hand end, a large gear wheel 8, this gear in turn meshing with a pinion gear 9, fast on the motor shaft of a motor 9a.

The housings I carry the adjustable centers for holding the crank shaft before it is gripped by a pair of driving ring gear chucks. The pair of housings ll form bearings, as will be described, for a pair of ring gear chucks. The housings III are split on their vertical diameters at their center on a line for assembly purposes and are held together when assembled by bolts H, and are bolted to the bed of the lathe by bolts l2, at the front and rear. These housings at their juncture have a groove in each half for a pin iii, the purpose of which is to align the interior bearing surfaces when the halves are bolted. together.

The rear half of the housings carry an upstanding boss ll, having a hole I! to permit the passage of a tire rod l6. Looking at Fig. 1, the interior construction of the housing is clearly shown. Secured to the interior circumference of the housings and, split as are the housings, are bronze bearing rings l1, furnishing a running surface for the ring gear chucks ill and I9, Figs. 1, 5, 6 and 7. These ring gear chucks, two in number, are substantially alike and the description of their construction and operation will be confined to the one at the left end of the lathe as shown in Fig. 1, and indicated by the ordinal ll.

These ring gear chucks, used for, holding the crank shaft securely in position to be worked on by the tools in conjunction with the centers as will be described, are also the driving means for tthglscrank shaft while it is being turned by the The construction of these ring gear chucks is obvious by looking at Figs. 5, 6 and I. being in the form of a wide face'd ring having on its outer surface a raised center portion 20, on which the gear teeth are cut, and a pair of flanged edges 2|, upon which rings 22 are riveted. Between the flanged edges II, and the raised center 2|, are bearing surfaces 23 fltting in the respective bearing rings II.

It will be seen, by looking at Fig. 7, that when the housings are assembled around these ring gear chucks, there is formed a circular path for the ring gear chucks to turn upon and that the flanged edges of the chucks together with the rings 22, fitting into grooves 20 in the side faces of the housings, form a dirt resisting joint, preventing, by the tortuous path formed, foreign matter getting into the bearing surfaces of the housing and ring gear chuck.

Looking at Figs. 5, 6 and '7, especially Fig. 5, it is noted that the ring gear chuck has an inwardly extending annular web portion 25 having a central opening 28, and a cutaway portion or gap at 21. The opening 26 in the web 25 is partially closed in each case by plates 28 screwed to the outer side of the ring gear chuck, this plate also having a cutaway portion 210, Fig. 6, which registers with the clearance space 21 in the web of the ring gear.

Looking now at Fig. 5, which is a view of the right hand side of the left ring gear chuck it, a stud 28, projects from plate 28. Mounted on this stud is a swinging clamp; member 30, which clamp member has a narrowed portion or nose 3!, the nose portion having a stepped taper block 32, indicated in dotted line, mounted in one edge. Projecting from the rear edge of the clamp member III, is a quadrant shaped-projection 88, having a slotted center, the slot having in its path a clamp bolt ll. Mounted in the inner edge of the swinging clamp member, is a self adjusting gripping member 35, this gripping member being located so as to grip the web of a crank shaft at a predetermined point. At a point below the center of the stud I! the clamp member has an extension 38 carrying a pin 38a; and in the web portion of the ring gear web is located a pin 31 and an extension coil spring 38 is attached to the two pins 36 and 31 as shown in the drawings. A second clamp member 38 is mounted on stud 29 and extended upward therefrom opposite clamp member 30, this second clamp member having a slotted upper end 40. Mounted in this slot!!! is a pivoted strain link or bar ll having a bifurcated end portion 42. Mounted across this bifurcated portion of the strain link, is a pin 42a having a portion at its center partially cut away to form a cam portion 43 shown in dotted line, Fig. 5. The clamp member 39 has mounted in its inner edge a self adjusting gripping member ll, so located as to grip a selected portion of a crank shaft.

Looking now at Fig. 6, which is the opposite side of ring gear chuck IS, the plate 28 has a stud l projecting from its face, on which stud is mounted a clamp arm 48, having a nose portion 46a with a stepped taper block similar to that in clamp member 30, on the opposite side of the chuck body. The clamp arm it also has a self adjusting grip member tic where it comes in contact with the upper web portion 69 of the crank shaft. Mounted on a pin 41, projecting from the plate 28, is a swinging grip block 48, having a slotted portion 19, with a pin 50 passing across the slot, and mounted on this pin is a strain link or bar 5|, having a cam pin 52, similar inconstruction to pin H in strain link 4!. The grip block 48 has a hardened projection 53 for gripping the work.

The plate 28 also has an L-shaped rib 54 at its lower portion, cast integral therewith. Screwed fast to the plate 28 and lying inside the rib 5| is a locating block 55, this block being capable of a fine final adjustment to position by set screws 58 at right angles to each other in rib 54, it only being necessary to loosen small screws passing in the plate 28 through slightly enlarged holes in the block 55 which allow the small movement by the set screws 56 necessary after which the small screws are again tightened. At 51 is a shoulder for a sidewise work locating point and at El are flat surfaces used also as work locating points vertically.

The method of placing a crankshaft in the lathe for turning will now be described. Mounted above the ring gear chuck is a rail 59 which is mounted (in columns 60 and has a trolley frame 6| adapted to run on the rail tracks. Mounted on the trolley is a fluid pressure cylinder 62 having the usual piston and piston rod, the lower end of the piston rod carrying a hook frame 5!, with hooks 6| on its lower edge which are adapted to engage a crank shaft at its midlength. An operating handle for the fluid pressure is shown at 65 and a pair of stops G6 and 61 are mounted on the rail.

All this and certain other details are clearly set forth in a Patent 1,700,721 to Groene, one of the present applicants.

A crank shaft 68 having the two opposite locating places 68a, milled on one edge of each of the end webs, is then placed in the hooks of the crane structur the trolley is pushed to a position against the stop 61, the crank shaft flange end brought forward over the nose 3| passing through ring gear chuck I 8. strikes the stop 61, the

at Au and Ab.

In this position, the operator manipulates the valve lever 65 on the trolley GI and the crank shaft is lowered to position with the locating spots 68a, resting on the locating surfaces 58 of the blocks 55. This places the centers of the crank shaft in a direct line with adjustable lathe centers 2 and the operator then manipulates the hand wheels 2a running the center pins to seats drilled in the ends of the crank shaft. The crane hooks are then disengaged and it is retracted to its idle position, shown in Fig. 1.

Look now at the right hand side of ring gear chuck l8, as shown in Fig. 5.

The shaft now being located in the position of attack for the tools, is to be clamped to the chucks as drivers, in the following manner. Both clamps, being in idle position are found, the one, 39 down against its stop 39a with its clamp bar 42 lying against the inside wall of the ring gear, while the front clamp 30 has been swung forward until the bolt 34 is at the inward extreme of the quadrant slot. It is to be understood that swing ing clamp 46 and the strain bar 5| on the opposite or left hand side as shown in Fig. 6 are also retracted, as is the swinging grip block 48, and the elements of the right hand chuck 19 are to be understood as being in like positions, so that the entry of the crank shaft is unobstructed by any of the gripping elements. Looking now at Fig. 6, the left hand side of ring gear chuck I 8, the operator will swing the clamp arm 46 down web portion 59, the spring 46b serving as a counterbalance only. He then brings the strain link up over the nose portion 450. and then inserts a wrench in the hexagonal socket in the end of the roller cam 52. As this cam is turned the cam portion in the center comes in contact with the inclined portion of the nose in and it brings to bear great pressure inward at the point where the portion 53 of the swinging grip block tends to move inward, thus clamps the crank shaft at its web portion against the opposite stop shoulder 51. At the same time the clamp arm 46 and its grip ping member 46c exert a very great pressure downward against portions 58 of the locating block 55.

The operator having firmly gripped the shaft on one side of the ring gear chuck I8, now brings into operation the gripping and driving means of the right hand side of the chuck l8, see Fig. 5. The operator brings both clamp arms 30 and 39. with their gripping means, in contact with the crank shaft, the gripping means engaging the crank shaft web at points 10, Figs. 5 and 8. The clamp members being in position against the enumerated contact points, the strain link H is of clamp member 38, bringing the roller cam portion of pin 42a in contact with the stepped piece 32. The pin is then rotated, bringing the high part of the cam toward the nose piece of clamp lever 30 and thus straining the clamp members toward each other, clamping the crank shaft securely between them. the gripper portions 35 and 44 of the two clamp members, in the course of the operation, having settled firmly into position, adjusting themselves perfectly to the crank shaft. Clamp bolt 34 is then tightened on the slotted segment 33, and the parts are locked in an immovable,

Looking now at Figs. 1, 2 and 3, a tool frame member H is securely bolted to the base I, by bolts 13, the frames being preferably of the type shown and dose in the Groene Patent 1,744 885, being constructed of spacer castings 14 and I5 and side plates 16 and II, the side plates being fastened to the sides of the upper and lower spacer castings by screws, as shown in Fig. 2. This forms a strong rigid structure with a high narrow tool bar space developed between them. To the bottom of the upper spacer casting is fastened a gib piece 18, this gib piece being fastened by bolts 19 at its rear end and being free for adjustment inward at the end towards the crankshaft. to take up wear in a set of tool bars.

M are in the form of wide. flat bars having considerable length and superimposed in relation to each other.

Each tool bar has a toothed, rearward extension 82 rod 58 before mentioned.

Mounted in the upper rear part of each of the tool frames is a short shaft 84, to which is secured a toothed lever arm 85 with a bifurcated outer end 86. The toothed portion of the arm 86 the tool bars and their tools in toward the work and to retract them therefrom.

It is also to be noted, looking at Figs. 1 and 3, that the center tool bars are of wider construction than those of the two ends, but that otherwise, the construction is the same.

The method and means for feeding the tool bars and their tools, will now be described. Looking with special reference to Figs. 2 and 3, the

Secured to the rearward extension and lying within the recess 81,15 a cylinder 90, having the usual piston and piston rod and with the usual admission ports in each end for the admission and exhaust of fluid. The extensions of the flanged casting 81. have recesses or slide ways 9| in each side, which ,ways have a gib piece 52 extending over part of the recesses forming a guide way for a toothed rack segment 93, the rack segment forming a continuation of the piston rod and being fastened thereto, and, to all intents and purposes, an integral part thereof.

It is manifest that any movement of the piston and piston rod will cause the rack segment 91 to slide in the ways 9|.

Secured to the rear of the base I in any sultabe and 95, these brackets to its length, a bifurcated projecting extension 9! bored to receive a pin M0. The toothed part of the segment arm 98 is in meshing contact with the teeth of the rack 93. A connecting link bar "I is in the form of a heavy square bar of steel, having at its upper end a turnbuckle I02, the outer one of the members of the turnbuckle having an eye III. The end 86 of the toothed lever arm has a bearing for a pin I04 passing through the eye I08 of the link bar IM and thus connecting a source of power to the middle tool bars and the tools.

It will be noted in Fig. 3, that the construction of the tool bar connections to the outer tool units I05 and I06 are the same as the one above described, with this exception, the arms I01 and I06 instead of having the toothed sector 96, are simple lever arms keyed to shaft 01. It is to be noted that in addition to being keyed to shaft 01 all the arms are split at one side as at I09, and clamped to the shaft by bolts, thus giving a construction capable of standing the great strains encountered in accomplishing the novel results of this machine.

Looking at Fig. 2, it is seen that, presuming the crank shaft is in rotation from any source of power applied to the drive shaft 5, (in this machine, a motor) if fluid pressure be admitted to the cylinder at the left hand end, the piston will start forward, carrying with it the rack 93, which in turn revolves the toothed segment arm 98, turning the shaft 61 and with it the arms I01 and I06, setting into motion the lever arms 05, and, through their toothed connection to the tool bars 8|, 82 the tool bars advance toward the revolving crank shaft.

It is also to be noted that when the chuck frames and the tool frames are all mounted on the bed I, that the bosses or lugs I4 for the chuck housings and bosses or lugs 63 for the tool frames are in line, and at this time the tie rod I6, threaded at both ends, is passed through the lugs, spacer bushings IIO being placed on the rods between the lugs so that when nuts are placed on the projecting ends of the tie rod and screwed down, the chuck housings and tool frames are securely clamped together thus preventing the stresses of operation from disarranging their spacing and adjustment and offering decided resistance to the spreading of the units when they are under work conditions.

Looking now at Fig. 41-

The Oilgear pump unit is shown at IIII. A brief general statement of the characteristics of this pump, a commercial product, is believed to be all that is necessary for a clear understanding of the power output and control thereof, as it is used in the machine of this application.

This pump has the capacity for supplying a rapid traverse and a series of adjustable feeds, forward and reverse, and consists of a high pressure variable delivery pump, a low pressure constant delivery gear pump, a control valve and a feed adjusting mechanism, all contained in one unit. The high pressure variable delivery pump is variable from 0 to 550 cubic inches per minute at a maximum pressure of 1000 lbs. per square inch. and the low pressure gear pump has a constant delivery of 3600 cubic inches per minute at a maximum pressure of 300 lbs. per square inch.

The pump is driven by separate electric motor which is in constant operation irrespective of the idle moments of the crank shaft machine of which it is an auxiliary.

Proceeding now with Fig. 4, a bracket. III is bolted to the side of the base and carries an electric switch In, which is provided with a handle II2 pivoted at H0. The shaft of switch Illa has a gear sector 4 fixed on it, and the handle II2 has a gear sector H5 meshing with the switch sector II4. This construction gives a quick operation to the contacts within the switch as is usual in this type of switch, which is well known commercially. The lever H2 has on its lower right side a lug II6 having a face in the form of an arc struck from the lever center, this lug having a slot III in said face.

A second lever III, pivoted at I I0 on the bed I, has an extension I20, extending to the right from its pivot H9 and carrying apin I2I in its outer end.

Located in a pocket I22, in the front of the base of the machine are gibs I20, forming a guide way for a cam carrying slide I24 on whose face is mounted a cam plate I26, the slide having rack teeth I26 on its lower edge. A spring I2I is so connected to lever extension I20 downward.

Looking now at Figs. 2, 3 and 4 for a moment:-

A shaft I20 extends from the recess I22 to a point outside the bed at the rear of the machine; a pinion gear I29 being secured on the front end and projecting in to the recess I22. At the opposite end, Fig. 2, to the rear of the machine is a bevel gear I36 meshing with a bevel gear III mounted on a short vertical shaft I32 in a bearing in the casting 00, this short shaft having a pinion I33 fast on its upper end in turn meshing with a rack I34 cut in the side of the rack bar 93.

Returning now to Fig. 4, it is to be noted that the pinion gear I20 is in engagement with the rack on the bottom of the cam carrying slide I24, and in this particular machine, the ratio between the rack segment 03 and the slide I24 is one to one, so that the same distances are traveled by the rack bar 06 and the cam carrying slide I24 whenever the rack segment is moved in either direction.

Lever II! has near its mid-length a pin I06 having a flat side I06 vertically where it projects from the lever II8, the flat side facing towards the right in Fig. 4. Mounted on a pivot on plate I I I is a latch I31, the right hand end of the latch lying on the pin I36 and having a left hand facing ledge or hook I36 adapted at certain positions of the latch, to engage the pin I66 at the right hand facing flattened portion I66. This latch also has a forwardly projecting lug I29 having a hole I40.

At a point near the handle portion, lever I" has an arm I, projecting to the left. Connected to this am is a link I42 engaging the top part of a double lever I46 carried in a bracket on the end of the bed I, the lower end of the lever having a link I44 engaging with the control valve stem I46 of the Oilgear pump IIO.

Leading from the Oilgear pump H0 is a pressure line I46 connecting with the left hand or rear end of the cylinder 60, and carrying to the cylinder the fluid pressure from either the gear 6 as to hold the lever pump or from the variable delivery pump, situated in the pump casing, according to the position of the valve, the various positions of the valve being determined by the position of the lever II6 either when it is moved by hand or by the cam plate I25 as will be explained presently. 65

Leading also from the pump is a fluid pressure line I41 which is connected to the right hand or forward end of cylinder 90.

Mounted on the front of the base I is a pressure cylinder I48 having a piston and piston rod 70 second relief valve I6I. Having a lower pressure 75 setting. this low pressure relief valve I5l discharges into the supply tank in the base of the pump, the line I52 leading from the relief valve I58 to relief valve I5I being also continued to the lower end of the cylinder I41.

The top of cylinder I48, has a line I53 leading into line I41.

Presume now the Oilgear pump motor in operation and the pump ready to deliver pressure from either the gear pump or the variable speed pump and presume that the crank shaft is tuming under the influence of its power plant, and that lever H2 is in running position at the right, thus bringing slot H1 in lug IIli on the lever H2 in line with safety pin Illa on lever I I8. This releases lever II8 for the movement, and the operator then moves lever H8 to the extreme left, moving the valve on the Oilgear unit and admitting oil to the system of pipes I46, I41 and their accessories. The oil pressure first admitted is from the gear pump section of the pump unit and is of lower pressur approximately 380 lbs. per square inch and of large volume. The first action of this oil pressure is to move the piston in cylinder 98 (Figs. 4 and 9) to the right at rapid traverse. The first result of this rapid movement is that the rack 83 moves the distance shown in the diagram, Fig. 9, and marked rapid traverse. When this movement takes place, the pin I2I, Fig. 4, enters the section of the slot in the cam plate I25 indicated by ordinal I 63, where it rides as the cam plate moves to the right under the influence of the pinion gear I29 and its drive. When the cam plate in its travel to the right reaches the point where section I54 of the cam begins, the pin is depressed by the dip in the cam and the lever H8 is shifted to the right for enough to cut out the gear pump supply and brings into action the supply from the variable feed section of the pump II8. During the rapid traverse movement an inspection of Figs. 2 and Swillshowthatthetoolbarsandtoolshave moved in toward the work, at rapid traverse, the distance indicated in Fig. 9. At this point the speed of the piston travel inward is at a predetermined accomplished rate of speed, by a setting of the pump valve. It is also to be noted from a. careful Inspection of the diagram, Fig. 9, that while the rate of piston speed remains constant for a given distance of travel, the rate of feed for the tools from this point to the finish is gradually, automatically, being reduced from the rate of feed furnished by the speed of piston travel to a rate furnished by the combination presented by the toothed segment arm 98, link bar ml and the lever arm 85. As the segment 88 approaches the zenith of rise of its arc, the lift on the link bar I8| becomes less and less and as it is with the segment 88, so, also it is with the lever arm which is also reaching toward the zenith of its travel and in consequence of the decrease in angularity of the arc of the centers from the vertical, the last step of the feedofthetoolsisreducedtoaverylimited movement inward in contrast to the degree of travel of the piston in cylinder 98.

Rwuming consideration of the movement of the piston in cylinder 88 and the cam plate, the pin I2I having reached the second dip in the cam down which It travels to the section of the slot marked I55, which is the fine feed section for the feed of the tools, the movement of the pin down the last incline correspondingly moves lever IIII further to the right, and effects a new setting of the pump valve, still further cutting down the variable delivery pump delivery.

All the above tends to a gradually slowing, fine feed for the tools while turning the bearings of the crank shaft, the coarse feed being used to turn the checks of the webs. Note in Fig. 4 an adjustable strip I58, which forms one side of the slot in section I55 of the cam. By adjustment the cam may be brought in perfect time with a stop I64 (Figs. 2 and 3) mounted on the rear of the base I in line with the central link bar I8I. When the link bar I8l strikes the stop I54 the piston has almost reached the end of its travel to the right and the further advance of the piston is stopped and with it, the further feed of the tools ceases; the pin I2I in the cam slot coming to a stop just clear of the end of the adjustable strip I56. During the time the lever IIB was to the left, the latch I31 has been riding on the top of the straight sided pin in lever II8. As the lever moved to the right, the latch finally came into engagement with the pin, this occurring just before the pin I2I reached the tip of the slot in section I 55 of the cam plate, the latched lever preventing the pin from dropping just as the feeding movement of the tools ceases. This leaves the tools in contact with the still turning crankshaft which is desirable for the purpose of sizing the pins, and for removing all tool marks.

When the piston stops, the pump continues to run at its last variable setting, and the pressure then commences to build up in the line I46, and when it reaches a predetermined point, relief valve I58 opens and the fluid passes through line I52 to the piston of the cylinder I48. During the entire period of the forward feeding cycle of cylinder 88 there is a low back pressure in lines I41 and I53, which pressure is exerted on the upper or rod end of the piston in cylinder I48. A second low pressure relief valve I5I in line I52 is set at a slightly greater pressure than the pressure existing in line I53 during the forward feeding cycle above mentioned. Thus fluid escaping through relief valve I58 will build up suflicient pressure in line I52 to overcome pressure in line I53, so as to cause the piston rod I 49 with adjustable collar "8a to rise until the end of the rod passes into the hole I48 in the lug of the latch I31.

When the collar strikes the lug I39, the latch releases the lever I I8 and it is retracted past the central neutral point until the pin I2I on lever extension I28 drops to the bottom of the cam plate groove. At the same time the variable delivery pump is out out by the valve on the pump unit and the gear pump out in as rapid traverse reverse. The direction of flow and the pressures are then reversed in the main lines I45 and I41. The pressure in line I46 is reduced to very low degree, the fluid returning into pump III] by being exhausted from port I45 of master cylinder 88. The pressure builds up in lines I41 and I 53 greater than in line I46 and also greater than the setting of the relief valve I5I. The result is that the piston in cylinder 98 is returned to the location shown in Fig. 2, thus retracting the tools at rapid traverse. Also. since pressure in line I53 is in excess of pressure setting relief valve I5I, piston rod I48 in cylihder I48 will be returned to its down position, exhausting the fluid in the lower end of this cylinder through the relief valve I5I.

When the pin I2I is reached by the cam surface at the end of cam plate I25, the lever is returned to the neutral position. When the lever I I8 passes the center when released by the latch, the pin H10 passes out of the slot H1 in lever H2 and this lever is returned to the stop position for the machine motor, thus stopping the chucks and the crank shaft. When the lever H2 reaches the neutral center position, the tools stop, the Oilgear pump is in neutral and the machine is ready for unloading.

The method of determining the time and amount of dwell of the tools for the purpose of sizing the pins and removing the tool marks and eccentricity therefrom, involves a consideration of the distance of the upward travel of the piston red I with its collar H90. in unit time, which distanceis known, as also is the number of revolutions of the work past the tools in unit time, which makes it easy to compute the number of revolutions of dwell of the tools relative to a given upward travel of rod 9. Thus the desired time of dwell of the tools is provided by adjusting the effective stroke of the rod I49, in this case by the desired location of the trip collar 9a.

After the tools have been returned from operating position and stopped automatically in their returned position as above described, the chucks are released, the crane is run in and lowered and has its hooks engaged with the shaft. The centers are run back, and the crane is operated to raise the shaft and run it to removal position to the right. The machine is then ready to be loaded for another cycle of operation.

The finished shaft is shown in Fig. 8. The parts shaded are those finished by the machine, being the flange A, the center bearings C, C, and the stub end D. The rough unfinished portions of the forging are indicated at B, B, B. It will be noted that the cheeks of the webs adjacent the turned cylindrical portions also are finished. This view also shows the finished areas of the sides of the webs, providing locating surfaces definitely related to a proper axis of the cylindrical portions, for locating the axis relative to the axis of the chucks, both longitudinally and transversely of the webs. It will be understood that after the chucks are clamped, with these locating surfaces bearing firmly on the locating surfaces of the chucks, the centers are relieved of the duty of holding the work piece in axial alinement with the chucks. Such a set up is far more reliable than one depending upon the centers, which at best have only limited areas of contact with the edges of the centering holes in the ends of the shaft. The centers are chiefly useful in holding the shaft preliminary to the gripp by the chucks.

Such locating areas on the sides of the webs, being limited in extent, permit of great clamping pressure and also a maximum of accuracy as compared with entirely finishing the sides and ends of webs, as was practised in early days before crank shaft forgings could be made of such close dimensions as at present, and required entire finishing for proper balance. Such locating also may be had, independent of the shapes of the webs.

What we claim as new and desire to secure by Letters Patent is:

l. A crank shaft lathe having in combination, means for holding a crank shaft in working position, tools adapted to be fed to the crank shaft, hydraulically operated mechanical means for feeding the tools toward the work rapidly to a point near the work, and said mechanical means having a movement reducing the rate of speed of feed of the tools when near the work with a constant supply of fluid to said hydraulic operating means.

2. A crank shaft lathe having in combination, means for holding a crank shaft in working position, tools adapted to be fed to the crank shaft, means for feeding the tools toward the work rapidly to a point near the work, said means comprising a combination of hydraulic and mechanical feeding means, said mechanical means having a movement for reducing the rate of speed of feed of the tools when near the work with a constant supply of fluid to the hydraulic portion of the feed actuating means.

3. A crank shaft lathe having in combination, means for holding a crank shaft in working position, tools adapted to be fed to said crank shaft, and means having an arcuate motion for feeding the tools toward the work rapidly to a point near the work, and a succeeding arcuate motion for reducing the rate of speed of feed of the tools when engaging the work for turning the bearings, and means for maintaining the tools at substantially the same radial distance for a definite period in which the bearings are sized and the tool marks removed.

4. A crank shaft lathe having in combination, means for holding a crank shaft in working position, tools adapted to be fed to said crank shaft, and means having an arcuate motion for feeding the tools toward the work rapidly to a point near the work, and a succeeding arcuate motion for reducing the rate of speed of feed of the tools when engaging the work for turning the bearings, means for maintaining the tools at substantially the same radial distance for a definite period in which the bearings are sized and the tool marks removed, and means for rapidly withdrawing the tools from the work.

5. A crank shaft lathe having in combination, means for holding a crank shaft in working position, tools adapted to be fed to the crank shaft, a cylinder and piston hydraulically actuated for feeding the tools to the work, having a connection to the tools with an arcuate movement feeding the tools toward the work rapidly to a point near the work, and reducing the rate of feed of the tools when near the work with uniform rate of travel of the hydraulically operated piston.

6. A lathe comprising a movable tool a hy draulic cylinder and a piston operating therein, a member driven thereby having a curved path of travel, and a connection from said member to the tool arranged so that the arc of movement of said member is so positioned relative to the path of the tool that said member provides variation in. the speed of the tool movement when the piston in said cylinder moves at a substantially constant rate of speed.

'7. In a crank shaft lathe, chucks to hold a crank shaft with its line bearings axially displaced from the chucks, tools slidable to and from the respective line bearings, fluid-actuated means to slide said tools, means to supply fluid under pressure to said fluid-actuated means. a cam member moved by said fluid-actuated mean a valve controlling said fluid-supply means, an operative connection from said cam to said valve, a latch for said connection, and fluid-actuated means to release said latch at a predetermined stage of operation of said cam member.

8. In a crank shaft lathe, chucks to hold a crank shaft with its line bearings axially displaced from the chucks, tools slidable to and from the respective line bearings, fluid-actuated means to slide said tools, a plurality of means to supply fluid under pressure to said fluid-actuated means, nection, and fluid-actuated means to release said each supply means supplying fluid under a dilierlatch at a predetermined stage of operation or ent pressure, a cam member moved by said fluid said cam member.

actuated meansa valve controlling said fluid sup- 14. In a crank shaft lathe, chucks to hold 9. ply means, an operative connection from said crank shaft with its line bearings axially discm to said valve to apply the different fluid pres placed from the chucks, tools slidable to and from sures, a latch for said connection, and fiuid-actuthe respective line bearings, mechanism operating ated means to release said latch at a predeterto provide successively a rapid traverse, a coarse 9. In a crank shaft lathe, chucks to hold a tinct from that operating said chucks, for operl0 crank shaft with its line bearings axially displaced ating said mechanism. from the chucks, tools slidable to and from the 15. In a machine tool, a movable work holder, respective line bearings, fluid-actuated means to a tool, fluid-actuated means to feed said tool tonection from said cam to said valve, a latch for tool from the work. said connection, and fluid-actuated means to re- 16. In a machine tool, a movable work holder, lease said latch at a predetermined stage of opera tool, fluid-actuated means to feed the tool tothe last mentioned fluid-actuated means. means, a valve controlling the fluid actuation, 10. In a crank shaft lathe, chucks to hold a an operative connection whereby said cam memcrankshaft with its line bearings axially displaced ber operates said valve, a latch maintaining the from the chucks, tools slidable to and from the position of said connection independently of said respective line bearings, fluid-actuated means to cam, means to stop the feeding, ,and means sure to said fluid-actuated means, a cam memthe work. her moved by said fluid-actuated means, a valve 17. In a machine tool, a movable work holder, controlling sa d fluid-suppl means, and an opa tool, fluid-actuated means to feed the tool to erative connection from said cam to said valve. ward the work, a. cam member moved by said In a crank Shaft l h Chucks hold a means, a, valve controlling the fluid actuation, an crank Shaft W its n bearings axially displaced operative connection whereby said cam member from said chucks, tools slidable to and from the operates said valve, a latch maintaining the no. pe iv lin earin fluidctuat d m s o sition of said connection independently of said slide said tools, means to supply fluid under relacam, means to stop the feeding, a. fluid-actuated tlvely low pressure to said flui means, device to release said latch, means to divert fluid me ns to supp y fluid u d d fl' relatively to said device after said stoppage, causing release 40 h p ss res 110 said flui means, of said latch for return of the tool from the work, m member m e by d fl t at d means, and relief means for said latch releasing device, & Valve controlling now of fluid from one the determining the rate of operation of said releash r of aid fl idpp y m a and at one or ing device and the time of return of the tool from another pressure from the second mentioned supt work 43 ply means, and an operative connection from In a crank shaft th h k t h 3 5911168111 Said Valvecrank shaft with its line bearings axially dis- In a Crank s t lathe. Chucks to hold placed from the chucks, a source of power for crank shaft with its line bearings axially disoperating said chucks, tools movable to and from placed from chucks, 0015 slidable t0 and from the respective line bearings mechanism pe -atin pressure to said fluid-actuated means, a 19, In a, crank shaft lathe, chucks to hold a means to release said latch at a predetermined mechanically connected to all of the tools and slide 581d means sllpply fluid under a single hydraulic motive means, a shaft rotated relatively low pressure to said fluid-actuated by said ti eans and a plurality of mechanme means to s pp fil-lld Under l t ical operative connections from said shaft to the atively high pressures to Said fl -M a e respective tools for feeding said tools to said means, a cam member moved by said fluid-actuhem-h1 5, 70 ated means, a valve controlling flow of fluid from 21. In a crank shaft lathe, means for chucking ical lever and link connections from said motive means to the respective tools for feeding said tools to the bearings.

22. In a crank shaft lathe, a plurality of chucks each comprising means for grippin the two crank webs between line bearings of a crank shaft, tools mounted to feed to said line bearings at the sides of the chucks, a single hydraulic motive means, and a plurality of mechanical operative connections from said motive means to the respective tools for feeding said tools to the bearings.

23. In a crank shaft lathe, a chuck comprising an outer rim, means on said rim for rotating said chuck, a locating block and pivoted clamping members within said rim on one side of said chuck, pivoted clamping members within said rim on the other side of said chuck, means for drawing said clamping members together at the opposide sides of the chuck, the interior of said chuck' being open between the two sets of clamping members at its opposite sides, and the means for drawing the clamping members together being adapted to be opened, whereby a crank shaft may be placed through said chuck with a crank in the opening thereof and having one web held against said locating block by the adjacent clamping members and the other web held between the clamping members at the opposite side of the chuck, exposing the line bearings of the crank shaft for turning, at the opposite sides of the chuck.

24. In a lathe comprising tool means and chucks relatively rotatable for turning the line bearings of a crank shaft having pairs of webs between line bearings, clamp devices comprised in said chucks to hold the shaft by clamping the respective pairs of webs, said clamp devices being so restricted in extent axially of the shaft as to expose all of the line bearings of the shaft for access of said tool means to said line bearings.

25, In a lathe comprising tool means and chucks relatively rotatable for turning the line bearings of a crank shaft having variously radially extended webs between line bearings, clamp devices comprised in said chucks to hold the shaft by clamping the respective webs, said clamp devices being variously radially positioned in said chucks to clamp the respective variously extended webs, and being so restricted in extent axially of the shaft as to expose all of the line bearings of the shaft for access of said tool means to said line bearings.

26. In a lathe comprising tool means and chucks relatively rotatable for mrning the line bearings of a crank shaft having variously shaped and variously radially extended webs between line bearings, clamp devices comprised in said chucks to hold the shaft by clamping the respective webs, being variously shaped and variously radially positioned in said chucks to clamp the respective variously shaped and variously extended webs, and being so restricted in extent axially of the shaft as to expose all of the line bearings of the shaft for a pair of said clamp devices being in each chuck, and each device of a pair being at a respective side of the chuck and being differently shaped and differently radially extended to clamp the webs of a respective pair, and being so restricted in extent axially of the shaft as to expose all of the line bearings of the shaft for access of said tool means to said line bearings.

28. In a lathe comprising tool means and chucks relatively rotatable for turning cylindrical portions of a crank shaft having pairs of webs between cylindrical portions, means comprised in each chuck, having abutment surfaces to engage respective sm'faces on a side of at least one of said webs of each pair, one abutment surface facing along the diametral length of the respective web to properly locate the cylindrical portions in the chucks along the length of the web, and the other abutment surface facing inward transversely of the respective web to properly locate said cylindrical portions in the chuck along a line transverse to the web, and clamp devices comprised in said chucks to hold the shaft by clamping the respective pairs of webs with said abutment surfaces sustaining the clamping pressure, said clamp devices being so restricted in extent axially of the shaft as to expose all of a series of axially alined cylindrical portions for turning.

29. In a chucking device to hold a crank shaft for turning a cylindrical portion of the shaft adjacent to a web of the shaft, a chuck body, abutment means on said body to engage a finished area on a side of the web, which area faces along the diametral length of the web, to properly locate the cylindrical portion in the device along the length of the web, spaced abutment means on said body to engage respective areas on opposite sides of the web, which areas face outwardly transversely of the web, to properly locate said cylindrical portion in the device along a line transverse to the web, and means to hold the device and the shaft together with said web areas and abutment means in efiective location-maintaining contact.

30. In a chucking device to hold a crank shaft for turning cylindrical portions of the shaft with the shaft substantially free from torsional distortion, by engagement with web portions thereof spaced longitudinally thereof, chuck bodies mounted and connected for synchronous rotation, each body having abutment means thereon to engage a finished area on a side of a respective web, which area faces along the diametral length of the web, to properly locate the cylindrical device along said length of the body having spaced abutment means thereon to engage respective areas on on posite sides of the web, which areas face outwardly transversely of the web, to properly locate the cylindrical portions in the device along lines transverse to the respective webs, .and means associated with the respective chuck bodies to hold the bodies and the shaft together with said web areas and abutment means in effective locationmaintaining contact.

31. The method of chucking a crank shaft for turning a. cylindrical portion of the shaft adjacent to a web of the shaft, which comprises abutment areas to the respective finished areas of the shaft web.

32. The method of chucking a crank shaft for turning cylindrical portions of the shaft by engagement with angularly alined webs of the shaft spaced longitudinally thereof, which comprises finishing areas in a definite relation to each other and to a proper axis of each cylindrical portion, one area on a side of each of said webs, which areas face along the diametral lengths of the webs, finishing areas in a definite relation to each other and to said proper axis, one area on a side of each areas to the respective finished areas of the shaft webs.

33. A chucking device as set forth in claim 29, in which the two abutment means at one side of the web, for engaging the web areas facing, respectively, along the length of the web and transversely outwardly of the web, are located in close adjacency in the device, for engaging the respective web areas when these areas are formed in close adjacency on the web of the shaft.

34. The method as set forth in claim 31, in which two areas are finished on the web, facing, respectively, along the length of the web and cutwardly transversely of the web, both on the same side of the web in close adjacency to each other.

35. As a novel article in an incomplete stage of a novel method of manufacture of the completed article, a work piece for forming a crank shaft, comprising a cylindrical portion and a web adjacent to the cylindrical portion, said work piece being prepared for chucking to turn the cylindrical portion, in that it is provided with a finished area on each side of the web, facing along the diametral length of the web in a definite relation to the proper axis of said cylindrical portion, and with a finished area on at least one side of the web, facing outwardly in a definite relation to said proper axis transversely of the web.

36. An article as set forth in claim 35, in which two of the areas, facing, respectively, along the length of the web and outwardly transversely of the web, are both on the same side of the web in close adjacency to each other.

37. As a novel article in an incomplete stage of a novel method of manufacture of the completed a work piece for forming a crank shaft, comprising cylindrical portions and webs adjacent the respective cylindrical portions, said work piece being prepared for chucking to turn the cylindrical portions, in that it is provided with a finished area on each side of each two webs substantially spaced along the shaft, which areas axis transversely of the webs, the correspondingly facing areas on the two webs also being in a definite relation to each other as well as to said proper axes of the cylindrical portions, for chucking with a minimum of torsional distortion of the work piece.

38. In a machine of the class described, tool feed movement, a hydraulic single-cylinder engine for tracting said carriage on its return stroke, a source of supply of oil under pressure connected to said engine through a valve, whereby it may be her to valve open retract position, a latch for holding said control member in valve closed position only against the force of said resilient means, and means actuated by the pressure built 39. In a machine of the class described, tool feed carriage control mechanism comprising in silient means urging said control member to valve open retract position, a latch for holding said control member in valve closed position only against the force of said resilient means, and means for tripping said latch.

40. In a machine of the class described, tool feed riage at one stroke and retracting said carriage on the return stroke, a reclprocable cam member connected to said carriage for movement therewith and having a cam slot, a reciprocable enfor tripping said latch means.

41. In a machine of the class described, carriage control mechanism comprising in combination, a carriage mounted for reciprocable movement, an engine for advancing said carriage at one stroke and retracting said carriage on the return stroke, a cam member connected to said carriage for movement therewith and having a cam slot, an engine control member having a cam follower coacting with said cam slot, resilient means urging said control member to engine retract position, latch means for holding said control member in engine stopped position only against the force of said resilient means, and means actuated by said engine for tripping said latch means.

42. In a machine of the class described, the combination of a pair of tool feed carriages, of means for advancing and retracting said tool feed carriages, comprising rack and pinion means connecting said carriages, whereby when one is advanced or retracted the other is similarly moved, an oil cylinder having a reciprocating piston, rack and pinion means connecting said piston to the upper tool feed carriage, an oil pump connected to said cylinder through a suitable control valve, means driving said oil pump, a cam member connected to said upper tool feed carriage and having a cam slot of substantially rectangular form having a valve opening, open, partially open, closing, closed, advance and retract control portions, a cam follower pin coacting with said cam slot, a control member carrying said pin and connected to said control valve, 9. pivoted keeper adapted to engage a lug on said control member to latch it in open position, resilient means urging said control member to closed position, and a piston operated trip for actuating said keeper to release said control member to stop the advance of said carriages and start their retraction, and means connecting said cylinder to a casing for said piston operated trip, whereby the pressure built up within said cylinder at the end of the stroke of said piston is transmitted to and operates said piston operated trip.

43. In a machine of the class described, the combination with tool feed carriages, of means for advancing and retracting said tool feed carriages, comprising means connecting said carriages, whereby when one is advanced or retracted the other is similarly moved, an oil cylinder having a reciprocating piston, means connecting said piston to the upper tool feed carriage, an oil pump connected to said cylinder through a suitable control valve, means driving said oil pump, a cam member connected to said upper tool feed carriage and having a cam slot, a cam follower pin coacting with said cam slot, a control member carrying said pin and connected to said control valve, a pivoted keeper adapted to engage a lug on said control member to latch it in open position, resilient means urging said control member to closed position, and a piston operated trip for actuating said keeper to release said control member tostop the advance of said carriages and start their retraction, and means connecting said cylinder to a casing for said piston operated trip, whereby the pressure built up within said cylinder at the end of the stroke of said piston is transmitted to and operates said piston operated trip.

44. In a machine of the class described, the combination with a plurality of tool feed carriages, of means actuating said tool feed carriages, comprising rack and pinion means connecting said carriages, whereby when one is actuated the other is similarly moved, a fluid cylinder having a reciprocating piston, rack and pinion means connecting said piston to one of said tool feed carriages, a fluid pump connected to said cylinder through a suitable control valve, means driving said pump, a cam member connected to one of said tool feed carriages and having a cam slot form having valve opening, open, partially open, closing, closed advance and retract control portions, a cam follower coacting with said cam slot, a control member carrying said follower and connected to said control valve, 9. pivoted keeper adapted to engage a lug on said control member to latch it in open position, resilient means urging said control member to closed position, and a piston operated trip for actuating said keeper to release said control member to stop the advance of said carriages and start their retraction, and means connecting said cylinder to a casing for said piston operated trip whereby the pressure built up within said cylinder at the end of the stroke of said piston is transmitted to and operates said trip.

45. In a machine of the class described, the

combination with a plurality of tool feed carriages, of means for actuating said tool feed carriages, comprising means connecting said carriages, whereby when one is actuated the other is similarly moved, a fluid cylinder having a reciprocating piston, means connecting said piston to one of said tool feed carriages, a fluid pump connected to said cylinder through a suitable control valve, means driving said pump, a cam member connected to one of said tool feed carriages and having a cam slot form having valve opening, open, partially open, closing, closed, advance and retract control portions, a cam follower coacting with said cam slot, a control member carrying said follower and connected to said control valve, a pivoted keeper adapted to engage a lug on said control member to latch it in open position, resilient means urging said control member to closed position, and a trip for actuating said keeper to release said control member, and means connecting said cylinder to a casing for said trip whereby the pressure built up within said cylinder at the end of the stroke of said piston is transmitted to and operates said trip.

46. In a machine of the class described, the combination of a pair of tool feed carriages, of means for actuating and retracting said tool feed carriages, comprising means connecting said carriages, whereby when one is actuated or retracted the other is similarly moved, means driving one of said carriages, control means therefor comprising a cam member connected to said one carriage and having an endless cam slot, a cam follower disposed in said slot, 8. reciprocable control member connected to said cam follower, resilient means urging said control member to closed position. means connecting said control member to said driving means, a pivoted keeper adapted to engage alug on said control member when the latter is moved to open position, and means for tripping said keeper to release said control member when said carriages reach the ends of their travel, whereby to cause said driving means to retract said carriage.

4'7. In a machine of the class described, the combination with a plurality of tool feed carriages, means for actuating and retracting said tool feed carriages, comprising means for connecting said carriages, whereby when one is actuated or retracted the other is similarly moved, means driving said carriages, and control means therefor, comprising a cam member connected to said one carriage and having an endless cam slot, a cam follower disposed in said cam slot, a reciprocable control member connected to said cam follower, resilient means urging said control member to closed position, means connecting said control member to said driving means, means adapted to engage said control member when the latter is moved to open position, and means for actuating said engaging means to release said control member when said carriages reach the forward ends of their travel.

48. In a machine of the class described, a control mechanism comprising in combination a reciprocable cam member having a cam slot, a. cam follower reciprocable normal to the movement of said cam member, a pivoted manual control lever removably connected to said cam follower, means connecting said manual control lever to a twoway control valve, resilient means urging said cam follower in one direction, means for latching said cam follower against the force of said resilient means, means for releasing said latch in response to the position of said cam member, a I

controlled member, means for driving said member, means connecting said controlled member to said cam member, and means associating said control valve to said driving means.

49. In a machine 01' the class described. a control mechanism comprising in combination a cam member having a cam slot, a cam follower, a pivoted manual control lever removably connected to said cam follower, means connecting said man- 10 ual control lever to a control valve, resilient means urging said cam follower in one direction, means for latching said cam follower against the force of said resilient means, means for releasing said latch in response to the position of said cam memher, a controlled member, means for actuating said member, means connecting said controlled member to said cam member, and means associating said control valve to said driving means.

F. GROENE. GEORGE W. LUNING.

DISCLAIMER Re. No. 19,905.W1llliam F. Groene and George W. Luning, Cincinnati, Ohio. CRANK- SHAFT LATHE. Patent dated March 31, 1936. Disclaimer filed July 27, 1938, by the assignee, The R. K. LeBlond Alas/mine Tool Co. Hereby enters this disclaimer to claim 19 in said specification.

[Ofiicial Gazette August 80, 1938.] 

